Oscillating slide machine

ABSTRACT

A controllable hydraulic oscillating slide machine includes an inner rotor arranged in a housing and having cylindrical recesses. A bearing is formed in the housing, in which a co-rotating outer rotor is mounted eccentrically to the inner rotor, the outer rotor having several pivotably suspended slide drivers that engage into the recesses of the inner rotor for rotationally driving the outer rotor by way of the inner rotor and form modifiable chambers. The slide drivers may each be coupled to a piston that is guided in a respective associated recess. A pressure level different from that in the chambers between the inner and the outer rotor may be set in the chambers delimited by the recesses and the associated pistons so that two different pressure levels may be generated and two different consumers can be supplied using the oscillating slide machine.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority to German Patent Application No. 102010 009 471.4, filed on Feb. 26, 2010; German Patent Application No. 102010 014 137.2, filed on Apr. 7, 2010; German Patent Application No. 102010 024 222.5, filed on Jun. 18, 2010; and WIPO Application No.PCT/EP2011/052352, filed on Feb. 17, 2011, each of which are herebyincorporated by reference in their entirety.

TECHNICAL FIELD

The present invention relates to a controllable hydraulic oscillatingslide machine according to the preamble of claim 1.

BACKGROUND

From DE 44 34 430 C2 a generic controllable hydraulic oscillating slidemachine comprising an inner rotor arranged in a housing and havingcylindrical recesses is known. Here, the inner rotor is rotatoricallyconnected to an outer rotor by way of so-called slide drivers, which ismounted in a bearing designed as control housing. The known oscillatingslide machine in this case is able to generate an exactly predefinedpressure independent of rotational speed. Such an oscillating slidemachine is usually employed for supplying bearing points in a combustionengine with lubricant.

SUMMARY

The present invention deals with the problem of stating an improved orat least an alternative embodiment for an oscillating slide machine ofthe generic type which is characterized in particular by an increasedfunctionality.

According to the invention, this problem is solved through the subjectof the independent claim 1. Advantageous embodiments are subject of thedependent claims.

The present invention is based on the general idea of designing ageneric oscillating slide machine in such a manner that two differentpressure levels can be made available with this oscillating slidemachine and because of this a supply of at least two different consumerseach with different pressure level is possible. With the oscillatingslide machine according to the invention, a lubricant supply of acombustion engine in a motor vehicle with a first pressure level and atthe same time a lubricant supply of a further consumer with a secondpressure level and/or another medium is possible for example. To do so,it was necessary in the past either to provide two different lubricantpumps, i.e. oscillating slide machines, or adjust the second pressurelevel for example by way of a throttling device. The controllable,hydraulic oscillating slide machine according to the invention comprisesan inner rotor arranged in a housing, which has cylindrical recesses(grooves). Here, so-called slide drivers engage in the recesses, whichwith their respective outer end are connected to the outer rotor forrotationally driving an outer rotor through the inner rotor and togetherwith the inner rotor and the outer rotor form modifiable chambers. Here,the slide drivers are pivotably suspended in the recesses of the innerrotor as well as in corresponding recesses of the outer rotor. Inaddition to this, a control for modifying the eccentricity between theinner rotor and the outer rotor and thus to modify a maximum possiblechamber volume can be provided, with the help of which the rate ofdelivery of the oscillating slide machine can be accurately set. It isnow substantial to the invention that the slide drivers are each coupledto a piston which is guided in a respective associated recess of theinner rotor. Here, a different pressure level can be set in the chamberswithin the inner rotor delimited by the recesses and the associatedpistons than in the chambers between the inner rotor and the outerrotor, as a result of which two different pressure levels can begenerated and because of this two different consumers can also besupplied with the oscillating slide machine according to the invention.This is not possible with the oscillating slide machines known up to nowand constitutes a substantial improvement of the functionality, sincefor realising two different pressure levels two oscillating slidemachines or supplementary throttling devices are no longer necessarynow, but the two pressure levels can be generated with the oscillatingslide machine according to the invention. This is of special advantagein particular in motor vehicle construction, since there it isfrequently demanded to supply different units with different lubricantpressures, wherein an available installation space in modern motorvehicles is usually so small that providing two different oscillatingslide machines as lubricating pumps is not possible or only withdifficulty so. Since the oscillating slide machine according to theinvention does not require any increase in installation space comparedwith generic oscillating slide machines, the oscillating slide machineaccording to the invention can be employed in place of previousoscillating slide machines but offers the major advantage of being ableto provide two different pressure levels. Providing these two differentpressure levels is easily possible in terms of design in this case, sothat the oscillating slide machine according to the invention does notproduce any or merely little additional costs.

With an advantageous further development of the solution according tothe invention, the individual slide drivers and the associated pistonsare each coupled to one another by way of a roller-shaped joint head anda fork/pincer-shaped joint mounting. Such a joint head and an associatedfork/pincer-shaped joint mounting allow an easily operable angulationbetween the slide driver and the associated piston, as a result of whicha very easy operation of the oscillating slide machine can be achieved.In addition, such joint heads and joint mountings are able to transmitboth compressive forces as well as tensile forces.

Further important features and advantages of the invention are obtainedfrom the subclaims, from the drawings and from the associated Figuredescription by means of the drawings.

It is to be understood that the features mentioned above and still to beexplained in the following cannot only be used in the respectivecombination stated but also in other combinations or by themselves,without leaving the scope of the present invention.

Preferred exemplary embodiments of the invention are shown in thedrawing and are explained in more detail in the following description,wherein same reference characters relate to same or similar orfunctionally same components.

BRIEF DESCRIPTION OF THE DRAWINGS

Here it shows, in each case schematically,

FIG. 1 a sectional representation through a first embodiment anoscillating slide machine according to the invention,

FIG. 2 a representation as in FIG. 1 however with an alternativeembodiment,

FIG. 3 in a schematic, perspective representation a furtherconfiguration of an oscillating slide machine,

FIG. 4 in a schematic, perspective detail representation at leastpartially a further configuration of an oscillating slide machine withslide drivers, wherein the slide drivers have rectangular pistons, and

FIG. 5 in a schematic, perspective detail representation at leastpartially a further configuration of an oscillating slide machine withslide drivers, wherein the slide drivers have round pistons.

DETAILED DESCRIPTION

According to FIGS. 1 and 2 a controllable hydraulic oscillating slidemachine 1 according to the invention comprises an inner rotor 3 arrangedin a housing 2 which comprises recesses 4 (grooves) that are cylindricalhowever not round but cuboid in shape. As is evident from FIGS. 1 and 2the inner rotor 3 in each case comprises six recesses 4, which areradially arranged. In general, the number of the recesses 4 however canbe any. The inner rotor 3 is connected to a driveshaft 5 in a positiveand/or non-positive manner, in particular in a rotationally fixedmanner. With the housing, a bearing 6 is additionally provided in whicha co-rotating outer rotor 7 is mounted eccentrically to the inner rotor3. The outer rotor 7 comprises a plurality of slide drivers 8 pivotablysuspended in said outer rotor, which engage in the recesses 4 of theinner rotor 3 for the rotational driving of the outer rotor 7 by theinner rotor 3 and form modifiable chambers 9. During the rotary movementof the inner rotor 3 the chambers 9 modify their volume and because ofthis ensure a delivery flow, for example a lubricant delivery, insofaras the oscillating slide machine 1 is designed as lubricant pump or asoil pump in a motor vehicle. Here, the oscillating slide machine 1generates a first pressure in the chambers 9.

According to the invention, the slide drivers 8 are now each coupled toa piston 10, which is translatorically guided in an associated recess 4of the inner rotor 3 each. In the chambers 11 delimited by the recesses4 and the associated pistons 10 a pressure level other than that in thechambers 9 between the inner rotor 3 and the outer rotor 7 can beadjusted, so that with the oscillating slide machine 1 according to theinvention, two different pressure levels can be generated and because ofthis two different consumers can be supplied. It is also conceivable ingeneral that in the chambers 11 another medium than in the chambers 9 ispumped. According to FIG. 1 the bearing 6 in this case is designed asrotary slide and accordingly can be rotated about an axis 12. A rotationof the bearing 6 in this case causes a change of the eccentricitybetween the inner rotor and the outer rotor 7 and because of this achange of the rate of delivery of the oscillating slide machine 1.Alternatively to this, the bearing 6, as is shown for example accordingto FIG. 2 can be designed as spherical bearing.

In order to make possible as easy an operation of the oscillating slidemachine 1 as possible, the slide drivers 8 and the associated pistons 10are coupled to one another via a roller-shaped joint head 14 and afork/pincer-shaped joint mounting each, wherein such a joint head 14 andsuch a fork/pincer-shaped joint mounting are not only able to generatetensile and compressive forces, but also offset directional deviationsbetween the piston 10 and the respective associated slide driver 8.Here, the recesses 4 in the inner rotor 3 can have an angular or,similar to a cylinder, a round cross section. In addition to this, aspring device which is not shown can be provided, which preloads thebearing 6 in a direction and because of this predetermines a certainvolume of the chambers 9.

The proposed oscillating slide machine 1 according to the invention alsoconstitutes a substantial improvement with respect to an internaltightness, wherein the oscillating slide machine 1 according to theinvention can be operated quasi as tandem pump for two differentpressure levels and/or media. This becomes possible in particularthrough the pistons 10 in the recesses 4 of the inner rotor 3 below theslide drivers 8, which are designed in such a manner that the innerleakage of the delivery medium from the chambers 11 to the chambers 9 isat least minimised. Here it is obviously likewise possible to deliver afluid or provide a corresponding pressure level merely by way of thechamber 9 or via the chambers 11.

A control of the oscillating slide machine 1 according to the inventionin this case is easily possible by rotating the bearing 6 designed aspivot bearing according to FIG. 1 or by sliding the bearing 6 designedas slide according to FIG. 2. However, it is likely to be of specialadvantage that with the oscillating slide machine 1 according to theinvention, two different pressure levels can be generated and because ofthis two different consumers can be supplied, which was not possiblewith previous oscillating slide machines because of the leakage betweenthe chambers 11 and the chamber 9. Here, the oscillating slide machine 1according to the invention does not require any enlarged installationspace so that it can be installed in the place of previous oscillatingslide machines.

The following embodiments relate to FIGS. 3 to 5, wherein theoscillating slide machine 1 in this case is designated as rotary slidepumping device 100. Further concordant terms and reference charactersare listed in the following table and can thus be synonymously used orreplaced by one another and used in FIGS. 1 to 5:

FIG. 1 and 2 FIG. 3 to 5 Reference Reference Term number Term numberOscillating slide machine 1 Rotary slide pumping 100, device 1600a,Oscillating slide pump 1600b, 1700a, 1700b, 200 Housing 2 Housing 300Inner rotor 3 Inner rotor 500, 1900 Recesses 4 Guide mounting 700,2100a, 2100b Driveshaft 5 Bearing 6 Holding ring 1200 Outer rotor 7Outer ring 400, 1800 Outer rotor 1100, 2700, 2900 Slide driver 8 Slide600, 2000 Oscillating slide 900, 2200 Oscillating piston rod 2400Chamber 9 First working chamber 800, 2900 Piston 10 Piston 2300a, 2300bChambers 11 Second working 1400, chamber 3000 Axis 12 Pivot axis 1300Guide path 13 Guide mounting 2100a, 2100b Joint head 14

The rotary slide pumping device 100 is connected to at least onehydraulic circuit (not shown), which serves for supplying an automaticor automated transmission (not shown) of a motor vehicle (not shown)with a pressure medium, in particular with an oil. The transmission inparticular comprises one or a plurality of friction clutches, which canbe hydraulically actuated with shifting elements and/or the transmissioncomprises further transmission components or shifting elements such asshifting sleeves or the like that have to be actuated. In particular,the transmission can be embodied as double clutch transmission havingtwo friction clutches. The friction clutches are designed in particularas wet-operating friction clutches. The friction clutches are cooled bythe oil. The use of dry clutches is also conceivable with atransmission, this is dependent on the respective embodiment. The rotaryslide pumping device 100 is designed as oscillating slide pump 200. Theoscillating slide pump 200 comprises a housing 300. Within the housing300, an outer ring 400 is arranged. The rotary slide pumping device 100furthermore comprises an inner rotor 500, which is rotatably mounted andcan be driven in a functionally effective manner by a motor that is notshown. The inner rotor 500 can be driven in particular by an electricmotor. Alternatively, the inner rotor 500 can be driven in afunctionally effective manner by an engine of the motor vehicle. Theinner rotor 500 is arranged within the outer ring 400. The outer ring400 is eccentrically arranged or can be eccentrically arranged relativeto the inner rotor 500. The outer ring 400 is preferentially arrangeddisplaceably or rotatably relative to the inner rotor 500.

The rotary slide pumping device 100 furthermore comprises a plurality ofslides 600. The slides 600 are arranged or can be arranged between theouter ring 400 and the inner rotor 400. The slides 600 extend betweenthe outer ring 400 and the inner rotor 500. The inner rotor 500comprises a plurality of guide mountings 700. The guide mountings 700substantially extend in radial direction. Within the guide mountings700, the slides 600 are guided. The width of the slides 600 is at leastpartially adapted to the width of the guide mounting 700. The slides 600in this case are oscillatingly guided in the guide mountings 700. Aplurality of first working chambers 800 are delimited by the outer ring400 and by the inner rotor 500 as well as by the slides 600.

FIG. 3 shows a configuration of the rotary slide pumping device 100,wherein seven slides 600 and thus seven first working chambers 800 areprovided. In an alternative configuration, more or fewer than sevenfirst working chambers 800 can be provided. The first working chambers800 are arranged between the inner rotor 500 and the outer ring 400. Theslides 600 delimit the respective first working chambers 800, which inpart are arranged adjacent to one another. The slides 600 and thus alsothe first working chambers 800 co-rotate with the inner rotor 500. Theguide mountings 700 are preferentially spaced identically on thecircumference. The slides 600 are guided radially displaceably in theguide mountings 700. The guide mountings 700 can be embodied as slits orbores (not designated in more detail). The guide mountings 700 can beembodied in particular as slits which are open at the edge on the faceend. Furthermore, the slides 600 are embodied as slide drivers 900,wherein the slide drivers 900 are pivotably mounted on the outer ring400. The slide drivers 900 are furthermore pivotably mounted in theguide mountings 700. The slide drivers 900 each comprise a head 1000,wherein the head 1000 is pivotably mounted on the outer ring 400. Thehead 1000 is rotatably mounted on the outer ring 400 in a functionallyeffective manner. The head 1000 has a part-cylindrical surface (notdesignated in more detail) or a cylinder segment area. The slide drivers900 are therefore pivotably mounted on the outer ring 400, in particularwith the head 1000. The slide drivers 900 in this case are substantiallyembodied conically, wherein a foot region (not designated in moredetail) of the slide drivers 900 comprises corresponding sphericalsegment areas or two opposing cylindrical segment areas, so that theslide driver 900 is pivotably mounted in the guide mountings 700. Theslide driver 900 in this case is substantially designed rigidly.

The outer ring 400 is designed in particular as outer rotor 1100,wherein the outer rotor 1100 is rotatably mounted. The outer rotor 1100is rotatably mounted in a holder 1200. The holder 1200 is preferentiallyarranged in a displaceable manner together with the outer rotor 1100, sothat the outer rotor 1100 together with the holder 1200 is displaceablerelative to the inner rotor 500. Because of this, the dimension of theeccentricity of the inner rotor 500 relative to the outer rotor 1100 isadjustable. Here, the holder 1200 can be pivoted about a pivot axis1300, wherein by pivoting the holder 1200 about the pivot axis 1300, therelative position of the outer ring 400 and of the outer rotor 1100 tothe inner rotor 400 can be adjusted. The first working chambers 800 canbe a pressure medium (not shown), in particular, a pressure medium canflow in and flow out here, in particular as a function of the currentposition feeding and discharge openings. The first working chambers 800are therefore usable for changing the pressure of the pressure medium. Afirst hydraulic circuit (not shown) can be supplied with the firstworking chambers 800. In particular, the first hydraulic circuit servesto supply specifically lubricate and cool the friction clutch (ES) withthe pressure medium, in particular with an oil or forlubricating/cooling other transmission components.

The disadvantages mentioned at the outset are now avoided in that theguide mountings 700 and the slides 600 delimit a second working chamber1400, wherein the second working chamber 1400 can be subjected to thethrough-flow of the pressure medium and the second working chamber 400can be used for changing the pressure and/or delivering the pressuremedium.

This has the advantage that with the second working chambers 1400 asecond hydraulic circuit can be supplied. The first hydraulic circuitcan be used in particular as low-pressure hydraulic circuit forsupplying the friction clutches with lubricating oil. The secondhydraulic circuit can be designed in particular as high-pressurehydraulic circuit for supplying the shifting elements of thetransmission. The volumetric change of the first working chamber 800 isgreater than the volumetric change of the second working chamber 1400during the operation of the rotary slide pumping device 100. Thepressure change realised by the second working chamber 1400 is greaterthan the pressure change realised by the first working chamber 800. Thesize of the second working chambers 1400 is substantially determined bythe stroke of the slides 600 and the cross section of the guidemountings 700. Through a suitable selection of the size of the guidemountings 700, the displacement volume/delivery volume realised by thesecond working chamber 1400 can be determined. The generatablevolumetric flow in the first working chamber 800 is substantiallydetermined by the size and the eccentricity of the outer ring 400relative to the inner rotor 500. Since the second working chambers 1400are provided within the inner rotor 500, the pressure levels/deliveryvolumes that can be tapped off the second working chamber 1400 arebetter adapted to the required pressure level for supplying the shiftingelements of the transmission. The first working chambers 800 arecompletely available for supplying the friction clutch with the pressuremedium. Here, the pressure medium serves as cooling oil/lubricating oil.Upon a rotation of the inner rotor 500, the first working chambers 800and the second working chambers 1400 are periodically increased andreduced in size. Because of this, a defined volumetric flow can begenerated in the first and second working chambers 800, 1400. The firstand second working chambers 800 and 1400 shown on the right-hand side ofFIG. 3 in this case have a large volume, and the first and secondworking chambers 800 and 1400 shown on the left-hand side of FIG. 3 havea small volume, since the inner rotor 500 in this case is positionednear the outer ring 400 and the slides 600 are thus pushed in deeplyinto the guide mountings 700. The first working chambers 800 areconnected in a functionally effective manner in particular to a coolingoil supply of a motor vehicle (not shown). The second working chambers400 are each connected in particular to a high-pressure hydrauliccircuit for actuating one or a plurality of shifting elements of thetransmission. The pressure medium for the first working chamber 800 ispreferentially sucked in from a first pressure medium reservoir (notshown) and the pressure medium for the second working chamber 1400 ispreferentially sucked in from a second pressure medium reservoir (notshown). The displacement volume and therefore the rate of delivery perrevolution are obtained from the displacement in the first workingchamber 800 between the inner rotor 500 and the outer rotor 400 and viathe stroke of the slides 600 in the guide mountings 700 or from thedisplacement in the second working chamber 1400. The first workingchambers 800 are preferentially supplied from the outside (radially oraxially). The first working chambers 800 can be supplied with thepressure medium through the outer ring 400 with pressure medium lineswhich are not shown or the pressure medium can be discharged by way ofthe pressure medium lines. The second working chambers 1400 within theinner rotor 500 can be preferentially supplied from the inside andsupplied and discharged via a hollow bearing pin 1500. Alternatively,the second working chambers 1400 can be supplied axially, in particularinsofar as the guide mountings 700 are designed open on the face end.With the preferred embodiment, the second working chambers 400 howeverare also supplied substantially radially. In the following, referencecan be made to FIGS. 4 and 5: since the configurations in FIGS. 4 and 5are similar, substantially corresponding components are provided withsame reference characters. FIGS. 4 and 5 partially show a rotary slidepumping device 1600 a and 1600 b respectively.

The rotary slide pumping device 1600 a and 1600 b is designed asoscillating slide pump 1700 a and 1700 b respectively. A housing and aholder are not shown in FIG. 2. The oscillating slide pump 1700 a, 1700b comprises an outer ring 1800, an inner rotor 1900 and a plurality ofslides 2000. The inner rotor 1900 in turn comprises a plurality of guidemountings 2100 a (see FIG. 4) and a plurality of guide mountings 2100 b(see FIG. 5), wherein the slides 2000 are guided in the correspondingguide mountings 2100 a or 2100 b. The guide mountings 2100 a (see FIG.4) are designed as slits (not designated in more detail). The guidemountings 2100 a are designed as slits that are open at the edge on theface end. In particular, the cross section of the guide mountings 2100 ais substantially rectangular. The guide mountings 2100 b (see FIG. 5)are designed as bores (not designated in more detail). The guidemountings 2100 b are embodied axially closed in the inner rotor 1900.The guide mountings 2100 b are designed closed axially or at the faceend. In particular, the cross section of the guide mountings 2100 b isround, substantially circular.

The outer ring 1800 is preferentially designed as outer rotor 2700. Theouter rotor 2700 comprises an outer circumferential surface 2800,wherein the outer rotor 2700 with the outer circumferential surface 2800is rotatably mounted in a corresponding holder (not shown, but see FIG.3). The slides 2000 are designed as slide drivers 2200, wherein theslide drivers 2200 are pivotably mounted on the outer rotor 2700. Theslide drivers 2200 are not designed rigidly. The slide drivers 2200comprise a piston 2300 a, 2300 b, wherein the piston 2300 a, 2300 b isguided in the guide mounting 2100 a, 2100 b. The cross section of thepiston 2300 a, 2300 b is adapted to the cross section of the guidemountings 2100 a, 2100 b or corresponds to the cross section of theguide mountings 2100 a, 2100 b. The slide drivers 2100 furthermore havean oscillating piston rod 2400 each, wherein the oscillating piston rod2400 is pivotably mounted on the piston 2300 a, 2300 b. The oscillatingpiston rod 2400 is furthermore rotatably mounted on the outer ring 1800in a functionally effective manner. The oscillating piston rod 2400 eachcomprises a head 2500, wherein the head 2500 is mounted in a bearingmounting 2600 in the outer ring 1800. The bearing mounting 2600 isopened towards the inner circumferential surface of the outer ring 1800not designated in more detail. The outer ring 1800 is arrangedeccentrically relative to the inner rotor 1900. The rotary slide pumpingdevice 1600 a and 1600 b respectively comprises a plurality of workingchambers 2900. Altogether, seven slide drivers 2200 and thus also sevenfirst working chambers 2900 are provided. The first working chambers2900 are delimited by the outer ring 1800, the inner rotor 1900 and theslides 2000. The first working chamber 2900 can be subjected to apressure medium through-flow. The first working chamber 2900 can be usedfor changing the pressure of the pressure medium. The first workingchamber 2900 can be connected to a first hydraulic circuit of anautomatic transmission (not shown). The first working chambers 2900 canbe supplied with a pressure medium via pressure lines that are notshown.

For example, the connections for directing and passing on the pressuremedium can also be arranged axially to the first working chamber 2900.The disadvantages mentioned at the outset are now avoided in that theguide mountings 2100 a, 2100 b and the slides 2000 delimit a secondworking chamber 3000, wherein the second working chamber 3000 can besubjected to a through-flow of the pressure media and the second workingchamber 3000 can be used for changing the pressure and/or delivering thepressure medium. The pressure change that is realised with the help ofthe second working chamber 3000 is preferentially greater than thepressure change realised by the first working chamber 2900. Thevolumetric change of the first working chamber 2900 in this case isgreater than the volumetric change of the second working chamber 3000during the rotation of the inner rotor 1900 relative to the outer ring1800. The first working chamber 2900 can in particular be connected to alow-pressure hydraulic circuit of the transmission. The second workingchamber 3000 can be connected to a high-pressure hydraulic circuit foractuating at least one shifting element of the transmission.

As has already been described in the configuration represented in FIG. 3the outer ring 1800 can be displaceably arranged relative to the innerrotor 1900. Because of this, the rate of delivery of the first workingchamber 2900 and of the second working chamber 3000 is adjustable. Thevolumetric change during a rotation of the inner rotor of the firstworking chambers 2900 and of the second working chambers 3000 isdependent on the eccentricity of the inner rotor 1900 relative to theouter ring 1800. In the configuration represented in FIG. 4, the pistons2300 a are designed as rectangular pistons. In the configurationrepresented in FIG. 5, the pistons 2300 b are designed as round pistons.

A leakage between the high-pressure region of the second working chamber3000 and low-pressure region of the first working chamber 2900 can bereduced or minimised in particular through the double rotatable mountingof the slide driver 22 or of the oscillating piston rod 2400 incombination with the pistons 2300 a, 2300 b. The embodiment with roundpistons in FIG. 5 has the advantage that the drag moment is reduced. Theface-end sealing of the first working chambers 2900 is preferentiallyeffected in that the face-end pump housings not shown in more detail arepressed together with a high axial force. Through the guidance of thepistons 2300 a, 2300 b within the inner rotor 1900, as is shown in FIG.5, the second working chamber 3000 is already delimited on the face endthrough the inner rotor 1900. Because of this, no high axial preloadduring the pressing together of the face-end pump housing is necessary.The advantage of using a oscillating slide pump 200, 1700 a, 1700 b (seeFIGS. 3 to 5) is that suction is possible from two separate pressuremedium reservoirs. The slide drivers 900, 2200 are pivotably mounted inthe outer rotor 1100, 2700. The mechanical friction within the rotaryslide pumping device 100, 1600 a, 1600 b is reduced through the designas oscillating slide pump 200, 1700 a, 1700 b. Because of this, thecomponent of the drive energy that is used for driving the rotary slidepumping device 100, 1600 a, 1600 b and the oscillating slide pump 200,1700 a, 1700 b is minimised. The rotary slide pumping devices 100 and1600 a, 1600 b can also be realised as rotary vane pump (not shown) inan alternative configuration. The slides designed as vanes in this caseare not connected to the outer ring. The outer ring is not arranged in aco-rotating manner relative to the inner rotor. The vanes are radiallyguided in the guide mountings. The sealing of the first working chambersis effected in that the vanes are pressed if required against the innercircumferential surface of the outer ring with a sliding shoe or thelike. Here, preferentially the first working chamber and the secondworking chamber are interconnected. The pressure from the displacementfrom the outer first working chamber is directed under the vanes inorder to press the vanes against the outer ring during the start-up ofthe inner rotor, thus establishing a seal between the vanes and theouter ring.

With the help of the rotary slide pumping device according to theinvention, different volumetric flows which are separated from oneanother can now preferentially be generated. On the one hand, for thecooling/lubrication of transmission and/or clutch components, highvolumetric flows in particular can be realised with low pressures and onthe other hand for the adjustment/actuation of shifting elements, lowvolumetric flows with high pressures can be realised. With the preferredembodiment of the rotary slide pumping devices according to FIG. 3 to 5shown here, the first working chambers, in particular for geometricalreasons, are used for realising the cooling oil volumetric flow and thesecond working chambers for realising the volumetric flow for actuatingthe shifting elements. It is also conceivable that for example withanother application a high pressure is requested with a high volumetricflow and a low pressure with a low volumetric flow, so that then ahigh-pressure hydraulic circuit could be supplied via the first workingchambers and a low-pressure hydraulic circuit via the second workingchambers. This is dependent on the respective application case and thespecific embodiment of the rotary slide pumping device or its connectionto respective further hydraulic components or hydraulic circuits.

In general, the invention according to FIGS. 3 to 5 relates to aoscillating slide machine, in the following called rotary slide pumpingdevice (100, 1600 a, 1600 b), in particular for at least one hydrauliccircuit of an automatic or automated transmission of a motor vehiclehaving an outer ring (400, 1800), having an inner rotor (500, 1900) andhaving a plurality of slides (600, 2000), wherein the outer ring (400,1800) is eccentrically arranged relative to the inner rotor (500, 1900),wherein the slides (600, 2000) are arranged or can be arranged betweenthe outer ring (400, 1800) and the inner rotor (500, 1900), wherein inthe inner rotor (500, 1900) comprises a plurality of guide mountings(700, 2100 a, 2100 b) and the slides (600, 2000) are guided in the guidemountings (700, 2100 a, 2100 b), wherein a plurality of first workingchambers (800, 2900) are delimited by the outer ring (400, 1800), theinner rotor (500, 1900) and the slides (600, 2000) wherein the firstworking chambers (800, 2900) can be subjected to a pressure mediumthrough-flow and wherein the first working chambers (800, 2900) can beused for changing pressure and/or delivery of the pressure medium. Here,the guide mountings (700, 2100 a, 2100 b) and the slides (600, 2000)each delimit a second working chamber (1400, 3000), wherein the secondworking chamber (1400, 3000) can be subjected to the pressure mediumthrough-flow and the second working chamber (1400, 3000) can be used forchanging the pressure and/or delivery of the pressure medium.

Further alternative or cumulative features of the rotary slide pumpaccording to the invention are:

-   -   that the second working chamber (1400, 3000) is connected to a        high-pressure hydraulic circuit,    -   that the pressure change realised by the second working chamber        (1400, 3000) is greater than the pressure change realised by the        first working chamber (800, 2900),    -   that the volumetric change of the first working chamber (800,        2900) is greater than the volumetric change of the second        working chamber (1400, 3000) upon a rotation of the inner rotor        (500, 1900),    -   that the first working chamber (800, 2900) is connected to a        low-pressure hydraulic circuit, in particular for cooling oil        supply of the automatic transmission,    -   that the outer ring (400, 1800) is designed as outer rotor        (1100, 2700), wherein the outer rotor (1100, 2700) is rotatably        mounted,    -   that the outer ring (400, 1800) is displaceably arranged        relative to the inner rotor (500, 1900),    -   that the slides (600, 2000) are designed as slide drivers (900,        2200), wherein the slide drivers (900, 2200) are displaceably        mounted on the outer rotor (1100, 2700), that the slide drivers        (2200) each have a piston (2300 a, 2300 b) and a oscillating        piston rod (2400), wherein the piston (2300 a, 2300 b) is guided        in the guide mounting (2100 a, 2100 b) and at least partially        delimits the second working chamber (3000), wherein the        oscillating piston rod (2400) is pivotably mounted on the piston        (2300 a, 2300 b) and pivotably mounted on the outer rotor (2700)        in a functionally effective manner,    -   that the guide mounting (2100 b) is embodied axially closed in        the inner rotor (1900),    -   that the piston (2300 a, 2300 b) is embodied as piston element        of a rectangular cross section or as round piston with a        substantially circular cross section,    -   that the first working chambers (800, 2900) and the second        working chambers (1400, 3000) are each connected to different        hydraulic circuits,    -   that the first working chambers (800, 2900) are connected to a        high-pressure hydraulic circuit and the second working chambers        (1400, 3000) to a low-pressure hydraulic circuit,    -   that the pressure medium for the first working chambers is        sucked in from a first pressure medium reservoir and the        pressure medium for the second working chambers from a second        pressure medium reservoir or suitably separated different        pressure medium reservoirs are provided.

1. A controllable hydraulic oscillating slide machine (pump or motor)comprising an inner rotor arranged in a housing, which comprisescylindrical recesses, a bearing formed in the housing, in which an outerrotor which co-rotates eccentrically to the inner rotor is mounted,which comprises a plurality of pivotably suspended slide drivers, whichengage into the recesses of the inner rotor for rotationally driving theouter rotor by way of the inner rotor and form at least one modifiablechamber, wherein the slide drivers are each coupled to a piston, whichis guided in a respective associated recess, wherein in chambersdelimited by the recesses and the associated pistons a pressure levelmay be set that is different from that in the at least one modifiablechamber between the inner rotor and the outer rotor, so that with theoscillating slide machine at least one of (i) two different pressurelevels may be generated and (ii) two different media may be delivered.2. The oscillating slide machine according to claim 1 wherein thebearing is designed as at least one of a pivot bearing and a slide. 3.The oscillating slide machine according to claim 2 wherein the pivotbearing is designed as spherical bearing.
 4. The oscillating slidemachine according to claim 1 wherein the slide drivers and theassociated pistons are coupled together via a roller-shaped joint headand a fork/pincer-shaped joint mounting each.
 5. The oscillating slidemachine according to claim 1, wherein the recesses have an angular or around cross section.
 6. The oscillating slide machine according to claim1, wherein a spring device is provided, which preloads the bearing in adirection.
 7. The oscillating slide machine according to claim 1,wherein the oscillating slide machine is designed as oil pump in a motorvehicle.
 8. The oscillating slide machine according to claim 1, whereinthe oscillating slide machine comprises six slide drivers.
 9. Theoscillating slide machine according to claim 1, wherein the volumetricchange of the at least one modifiable chamber or of a first workingchamber is greater than the volumetric change of the chamber or of asecond working chamber upon a revolution of the inner rotor.
 10. Theoscillating slide machine according to claim 9, wherein the firstworking chamber or the at least one modifiable chamber is connected to alow-pressure hydraulic circuit.
 11. The oscillating slide machineaccording to claim 9 claim, wherein the recesses or a guide mounting areembodied axially closed in the inner rotor.
 12. The oscillating slidemachine according to claim 11 wherein a slide driver comprises a pistonand an oscillating piston rod, wherein the piston is guided in the guidemounting and at least partially delimits the second working chamber,wherein the oscillating piston rod is pivotably mounted on the pistonand pivotably mounted on the outer rotor in a functionally effectivemanner.
 13. The oscillating slide machine according to claim 1 whereinthe piston is embodied as piston element of a rectangular cross sectionor as round piston with a substantially circular cross section.
 14. Theoscillating slide machine according to claim 9 wherein the pressuremedium for the first working chamber or the at least one modifiablechamber is sucked in from a first pressure medium reservoir and thepressure medium for the second working chamber or the chambers is suckedin from a second pressure medium reservoir or corresponding separatedifferent pressure medium reservoirs are provided.
 15. The oscillatingslide machine according to claim 1, wherein the recesses or a guidemounting are embodied axially closed in the inner rotor.
 16. Theoscillating slide machine according to claim 9, wherein the firstworking chamber or the at least one modifiable chamber is connected to alow-pressure hydraulic circuit, and wherein the recesses or a guidemounting are embodied axially closed in the inner rotor.
 17. Theoscillating slide machine according to claim 16 wherein a slide drivercomprises a piston and an oscillating piston rod, wherein the piston isguided in the guide mounting and at least partially delimits the secondworking chamber, wherein the oscillating piston rod is pivotably mountedon the piston and pivotably mounted on the outer rotor in a functionallyeffective manner.
 18. The oscillating slide machine according to claim17 wherein the pressure medium for the first working chamber or the atleast one modifiable chamber is sucked in from a first pressure mediumreservoir and the pressure medium for the second working chamber or thechambers is sucked in from a second pressure medium reservoir orcorresponding separate different pressure medium reservoirs areprovided.
 19. The oscillating slide machine according to claim 16wherein the pressure medium for the first working chamber or the atleast one modifiable chamber is sucked in from a first pressure mediumreservoir and the pressure medium for the second working chamber or thechambers is sucked in from a second pressure medium reservoir orcorresponding separate different pressure medium reservoirs areprovided.
 20. The oscillating slide machine according to claim 3 whereinthe slide drivers and the associated pistons are coupled together via aroller-shaped joint head and a fork/pincer-shaped joint mounting each.